Re-spooling machine



, w. KURSINCZZKY Oct. 3, 1967 RE-SPOODING MACHINE 7 Shee tsSheet 1 FiledDec. 18, 1964 William Kurs/hczky INVENTOR'.

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Oct. 3, 1967 v w. KURSIN'CZKY 3,345,005

RE-SPOOLING MACHINE Filed Dec. 18, 1964 7 Sheets-Sheet 5 Fig. 3

William Kurs/nczky 1. VENTOR,

WWW Fm Oct. 3, 1967 w. KURSINCZKY RE-SPOOLING MACHINE 7 Shets-Sheet 4Filed Dec.

William Kursinczky INVENTQR. 1

Oct. 3, 1967 w. KURSINCZKY RE-SPOOLING MACHINE 7 Sheets-Sheet 5 FiledDec. 18, 1964 William Kurs/nczky INVEN'IOR.

BY M

Oct. 3, 1967 w. KURSINCZKY RE-SPOOLING MACHINE 7 Sheets-Sheet '6 FiledDec. 18, 1964 u m m N r m 1 E m W %m Q%\ m v Q E E m M @Q m Y 9w B Oct.3, 1967 w. KURSINCZKY 0 RE-SPOOLING MACHINE Filed Dec. 18, 1964 7Sheets-Sheet 7 Mil/am Kursinczky 1N VEN TOR. 1

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United States Patent 3,345,005 RE-SPOOLING MACHINE William Kursinczky,118 Wedgewood Ave., Woodbridge, NJ. 07095 Filed Dec. 18, 1964, Ser. No.419,371 Claims. (Cl. 242-45) ABSTRACT OF THE DISCLOSURE A machine forre-spooling wire by simultaneously rotating and axially reciprocatingthe spindle on which a spool is mounted, tension of the wire beingmaintained substantially constant by regulating the torque transmittedto the spindle and the speed with which the spindle is reciprocated. Thetorque transmitted is regulated by both slippage in a slip clutchthrough which power is transmitted to the spindle and the reciprocatorymechanism and the drag imposed by a brake through which power isabsorbed.

This invention relates to a machine for re-spooling wire or the like andmore particularly to a heavy-duty power transmitting device throughwhich a winding spool or drum may be continuously rotated and axiallyreciprocated in order to wind wire thereon under a constant tension.

One of the major achievements of the present invention is the provisionof a machine through which a relatively large spool or winding drum forwire may be rotated at a relatively high speed and yet wind the wirethereon with a substantially constant tension the driven spool alsobeing cyclically reciprocated at it is continuously rotated in order toaxially distribute the wire being wound thereon.

It is generally known that electromagnetically operated devices may beemployed for torque controlling purposes in a winding operation in anattempt to regulate wire tension.

When dealing with relatively large wire winding spools that arereciprocated, there is a considerable problem involved in maintainingconstant wire tension and imparting reciprocation to the driven memberwhile it is being rotated at a relatively high speed because of the highaccelerating forces involved and their effect on the transmission parts.Because of the arrangement of parts and the design of the componentswhich form the machine of the present invention, the foregoing problemshave been successfully dealt with.

It is therefore an important object of the present invention to providea transmission through which power from a constant source of motivepower is controllably supplied to a driven spindle at a speed varied inorder to maintain a constant torque on the load to which the spindle isconnected, which load is continuously varied as would be the case whenwire is being wound upon a spool to which the spindle is connected.

In accordance with the foregoing object, an additional object of thepresent invention is to provide a slip clutch and drag brake assemblythrough which power is transmitted and absorbed to control the powerdelivered to the driven spindle member. The relative slipping of thecoupling clutch and drag brake is automatically controlled utilizing ina novel arrangement, magnetic means of a type which automaticallyadjusts for changes in flux gap due to wear.

A still further object of the present invention is to provide a powertransmitting train through which continuous rotation as well as axialreciprocation is imparted to a driven spindle member at relatively highspeeds.

3,345,905 Patented Oct. 3, 1967 An additional object of the presentinvention is to provide a reciprocating drive mechanism associated witha continuously rotated driven spindle capable of coping with the highaccelerating forces involved.

These together with other objects and advantages which will becomesubsequently apparent reside in the details of construction andoperation as more fully hereinafter described and claimed, referencebeing had to the accompanying drawings forming a part hereof, whereinlike numerals refer to like parts throughout, and in which:

FIGURE 1 is a perspective view of the machine of the present invention.

FIGURE 2 is a perspective view of the machine as viewed from anotherangle.

FIGURE 3 is a top sectional view of the machine shown in FIGURES 1 and2.

FIGURE 4 is a sectional view taken substantially through a planeindicated by section line 44 in FIG- URE 3.

FIGURE 5 is a sectional view taken substantially through a planeindicated by section line 5-5 in FIG- URE 4.

FIGURE 6 is a rear elevational view of the machine shown in FIGURES 1and 2.

FIGURE 7 is a simplified perspective view of the drive train associatedwith the machine.

FIGURE 8 is an enlarged partial sectional view of a portion of themachine as illustrated in FIGURE 4.

FIGURE 9 is a partial sectional view taken substantially through a planeindicated by section line 99 in FIGURE 8.

FIGURE 10 is a partial sectional view taken substantially through aplane indicated by section line Ill-10 in FIGURE 9.

FIGURE 11 is an enlarged partial sectional View of a portion of themachine illustrated in FIGURE 5.

FIGURE 12 is a partial sectional view taken substantially through aplane indicated by section line 1212 in FIGURE 11.

Referring initially to FIGURES 1, 2 and 6, it will be observed that themachine generally referred to by reference numeral 10, includes ahousing frame assembly generally referred to by reference numeral 12adjustably positioned on a supporting surface or floor by means of atrack frame assembly generally referred to by reference numeral 14. Thehousing frame assembly 12 includes four vertical frame posts 16interconnected at the lower ends, by a supporting platform 18 and byhorizontal frame members 20 at the upper ends. Also, interconnecting thevertical posts 16 intermediate the upper and lower ends thereof, is asecond supporting platform 22 on which there is carried a reciprocatingdrive mechanism generally referred to by reference numeral 24 as well asa pair of slide journal assemblies 26 and 28 by means of which an outputspindle member 30 is supported for continuous rotation and axialreciprocation. The spindle 30 is adapted to be connected to a wirewinding spool 32 as shown by dotted lines in FIGURES 1 and 2. Power fordriving the spindle 30 is derived from an electric gear motor assembly34 mounted in fixed position on the base platform 18. The base platformalso supports power transmitting facilities through which the power istransmitted to the spindle 30 for continuous rotation thereof as well asto the reciprocating drive mechanism 24.

In order to adjustably position the housing frame assembly 12 and thedriven spindle 30 projecting forwardly therefrom, each of the verticalposts 16 have connected to the lower ends thereof, supporting wheelassemblies 36 guided for movement along a pair of parallel spaced trackportions 38 which extend upwardly from the positioning track assembly14. A positioning screw 40 is therejournal bracket 42 fixedly mounted onthe forward end of the track assembly. The positioning screw isthreadedly received through a nut assembly 44 mounted on the platform18. Accordingly, the housing frame assembly 12 may be displaced alongthe track portions 38 by rotation of the screw member through the handcrank 46 between limits established by the limiting nuts 48 and 50. Oncethe housing frame assembly has been positioned to the desired location,it may be fastened to the floor by means of bolts extending through theanchoring flanges 52 secured to the opposite sides of the base platform18 adjacent the track portions 38.

After the housing frame assembly has been locked in adjusted position toproperly align the driven spindle 30 and the wire winding spool 32mounted thereon, with the source of wire, depending upon the size andshape of the winding spool, its reciprocating speed may be adjustedthrough the adjusting handwheel 54 which projects forwardly from thehousing assembly while the reciprocating stroke may be adjusted by meansof the stroke adjusting handwheel 56 which projects laterally from theside of the housing assembly as shown in FIGURE 1. An endless belt drive58 transmits the power from the gear motor assembly 34 to both thedriven spindle 30 for rotation thereof and to the reciprocating drivemechanism 24 adjusted by means of the handwheels 54 and 56. Toward thislatter end, an endless belt drive 60 is mounted rearwardly of thehousing assembly as shown in FIGURE 6 for transmitting power to thedriven spindle connected to the driven pulley 62 for continuous rotationthereof. A drive pulley 64 is driven by the power transmittingfacilities so as to impart continuous rotation through the belt drive 60to the driven spindle 30. A second belt drive 66 having a belt tightener68, is also disposed rearwardly of the housing assembly drivinglyinterconnecting the drive pulley 70 with the driven pulley 72 in orderto supply power at a reduced speed to the reciprocating drive mechanism.

Referring now to FIGURE 7, it will be observed that the endless drivebelt 58 transmits power from the electric gear motor assembly 34 to anintermediate power shaft 74 to which the driven pulley 64 is connectedso as to transmit continuous rotation to the driven spindle 30 by meansof the belt drive 60. Also connected to the power shaft 74, is a drivepulley 76 drivingly connected by means of the endless belt drive 78 to adriven pulley 80 connected to the input shaft 82 of a ten to onereduction drive assembly 84 of a conventional type. The reduction ratioof the reduction drive assembly 84 may therefore be varied through theratio adjusting handwheel 54 aforementioned in order to control thespeed of the drive pulley 70. The drive pulley 70 thereby impartsrotation to the cam shaft 86 associated with a reciprocating driveassembly 24 at a regulated reduction drive ratio through the endlessbelt drive 66. The reciprocating drive mechanism 24 is thereby operativeto impart reciprocation to the driven spindle 30 as it is beingcontinuously rotated.

Referring now to FIGURES 3, 4 and in particular, it will be observedthat the cam shaft 86 is rotatably mounted above the upper platform 22between the journal assemblies 88 and 90, the cam shaft projectingrearwardly beyond the journal assembly 90 for connection to the drivenpulley 72 as aforementioned. The cam shaft is provided with a pair ofspiral grooves 92 and 94 having helix angles inclined in oppositedirections so as to cause linear movement of a reciprocating followerdevice 96 in response to uni-directional rotation imparted to the camshaft. The recipr-ocatory speed of the reciprocating drive mechanismwill thereby be governed by the speed of the driven pulley 72, thisspeed in turn being regulated through the variable speed, reductiondrive assembly 84 aforementioned. Although the stroke of the followerdrive 96 is fixed along the cam shaft 86, the reciprocatory strokeimparted to the spindle may be varied by the adjustable positioning of afulcrum block 98 which pivotally mounts a lever rod 100. Accordingly,the lever rod 100 is pivotally connected by the yoke 102 at one end tothe follower device 96 and at the opposite end it is operativelyconnected by the pivotal slide yoke 104 to a bearing sleeve member 106through which the spindle 30 extends. The sleeve member 106 is thereforeaxially positioned on the spindle 30 between a pair of collar members108 through which axial thrust is transmitted to the spindle. Each ofthe journal assemblies 24 and 26 therefore include roller bearings 110and slide bearings 112 through which the spindle 30 extends. The sleevemember 106 through which axial movement is imparted to the spindle, hasa pair of pivot elements 114 extending through slots 116 in the yokemember 104 to which the lever rod 100 is connected. Accordingly, as thelever rod 100 is oscillated about a vertical axis established throughthe fulcrum block 98, by means of the reciprocating follower device 96,axial reciprocation will be imparted to the spindle 30. By controllingthe position of the fulcrum block 98, the reciprocation ratio and hencethe stroke of the spindle 30 may be regulated. The stroke adjustinghandwheel 56 is therefore connected to a positioning screw member 118rotatably mounted above the platform 22 by the bearings 120 and theslide adjusting bracket 122. A nut member 124 is threadedly mounted onthe screw adjustment member 118 for slidable displacement along theadjustment screw 118 when rotated by the handwheel 56. The adjustmentnut 124 is pivotally connected by the pivot connection 126 to thefulcrum block 98 through which the lever rod 100 slidably extends.Accordingly, the fulcrum block 98 may be slidably positioned so as toestablish a pivotal axis through the pivot connection 126 aligned withthe pivot connection 128 through which the fulcrum block is also guidedfor positioning movement by a top guide member 130 as shown in FIGURE 5.

Referring now to FIGURES 5, 11 and 12, it will be observed that thelever rod 100 is pivotally connected by the yoke member 102 to thefollower device by means of a pair of pivot connections 132 establishinga pivotal axis which intersects the axis of the cam shaft 86. Thefollower device includes a slide block 134 threadedly receiving thepivotal connecting elements 132 and also being provided with a bore 136through which the cam shaft 86 extends. Also formed in the block 134, isa laterally extending bore 138 which intersects the bore 136. A grooveengaging element 140 is rotatably mounted within the bore 138 about apivotal axis established by the threaded stud 142 projecting inwardlyfrom the cover plate 144 secured by fasteners 146 to the block 134. Thegroove engaging element is provided with an arcuate tooth portion 148having a radius of curvature as shown in FIGURE 11, corresponding to theroot diameter of the cam shaft 86 so that the tooth portion may bereceived within the spiral groove 22 and 94 without interference. Thetooth portion 148 also tapers inwardly in non-radial relation to the camshaft and has a maximum thickness at the pivotal axis establishedthrough the stud 142 as more clearly seen in FIG- URE 12. In thismanner, the axial direction of the follower device may be reversed atthe end of its stroke by pivotal displacement of the follower element140 about its pivotal axis, transferring the tooth portion 148 from onespiral groove to the other without interference.

Referring now to FIGURES 4 and 5, it will be observed that the beltdrive 58 drivingly connects the drive pulley 158 to a driven pulley 152,the drive pulley being connected to the output shaft 154 of the gearmotor assembly 34 from which a constant source of power is derived. Thedriven pulley 152 is rotatably mounted on the intermediate power shaft'74 rotatably supported by the journal bearing assemblies 156, 212 and158. The assembly '156 is supported in proper position by the suspensionplate 160 secured to the platform 22 while the rearward journalassemblies 212 and 158 are supported in proper position by means of thehanger structures 210 and 162 projecting downwardly from the platform 22as shown in FIGURE 4. The driven pulley 152 is secured to a drive member164 supported for rotation on the forward portion 165 of power shaft 74.The power shaft 74 is provided with spaced splined portions 166, 168 and17 0 for rotatively connecting the power shaft to a slip clutch andbrake assembly 172, and to the drive pulley wheels 76 and 64aforementioned. The slip clutch and brake assembly 172 is therebyoperative to regulate the power transmitted to the drive pulleys 76 and64 for the purposes of the present invention.

Referring now to FIGURES 8, 9 and in particular, it will be observedthat the drive member 164 is associated with a clutch and brake assembly172 including a slip coupling clutch unit 173 supported for rotation onthe power shaft 74 by the drive member 164 having spaced needle bearings174 lubricated by lubricant supplied through the bore 176. The drivemember is also held in axially fixed position on portion 165 of thepower shaft by means of the bearing assembly 156 separated from oneaxial end of the drive member by the thrust washer 178, the oppositeaxial end of the drive member abutting a second thrust washer 180 whichis seated against the shoulder 182 formed on the power shaft. The drivemember includes an externally splined portion 183 axially spaced fromthe driven pulley member 152 for mounting a clutch armature disk 184.The clutch disk carries therewith a plurality of circumferentiallyspaced magnetic flux conducting elements 186 and is spaced by a smallflux gap from the forward axial face 188 of a torque absorbing clutchmember 190 when disengaged. The clutch disk 184 is provided with aplurality of circumferentially spaced spring elements 192 Which projectradially inwardly into engagement with the drive member. Thus, theclutch disk 184 is magnetically attracted to and held in engagement withthe slip clutch member 190 against the spring bias of the springelements 192 through the magnetic elements 186 by electromagnetic means(not shown). In this manner, a continuous axial bias will be imposed onthe slip clutch member when transmitting torque to yieldably hold it infrictional engagement with a driven conical member 194-. The drivenconical member 194 is therefore splined to the power shaft 74 along thespline portion 166 and is limited in axial displacement in one directionby the thrust washer 180. The axial bias imposed on the slip clutchmember therefore causes it to engage the driven member while permittingslippage when transmitting rotation to the power shaft.

Because of the foregoing arrangement any change in the flux gapresulting from slippage wear will be compensated for by advancement ofthe faces on the disc 184 toward the clutch member 190. This type offlux gap compensating feature is embodied in clutch and brake unitsidentified as Dyna-Torq spline drive Model 312, manufactured byDynamatic Division of Eaton Manufacturing Co., of Kenosha, Wisconsin, asshown in its bulletin dated May 31, 1962, also described in its pamphletEaton Dyna- Torq Stationary Field Clutches and Clutch-Couplings, thedetails of which form no part of the present invention. A hearing sleeveelement 200 is received within the socket 196 of the clutch memberforming a radially inner bearing race for the ball elements 195 andaxially spacing the conical drive member 194 from a second conicaldriven member 202 associated with a drag brake unit 204.

The drag brake unit is similar in construction and operation to the slipclutch unit 173 and includes a stationary, torque absorbing brake member206 through which power is absorbed in order to reduce and stoptransmission of power through the power shaft to the driven spindle andthe reciprocating drive mechanism. The brake member 206 may therefore befixed in any suitable fashion to a plate 208 which in turn may besecured to the hanger struc-' ture 210 suspending the bearing assembly212. The brake member 206 is made of magnetic material similar to theslip clutch member 190 and is similarly spaced by a flux gap fromcircumferentially spaced magnetic elements 214 carried by a brake disk216. The brake disk is internally sp lined to the externally splineddrag member 218 having a conical bore receiving the conical member 202for frictional engagement therewith. The brake disk 216 is similar inconstruction to the clutch disk 184 and hence includes a plurality ofspring elements 220 which engage the spline disk member 218. The springelements 220 and magnetic elements 214 when engaging the brake member206 are thereby operative to yieldably bias the disk member 218 in arearward direction as well as maintain the flux gap fixed prior toengagement without any need for adjustment. Accordingly, the biasimposed on the disk member 218 during engagement will permit slippage ofthe mem her 218 relative to the conical member 202 since it may beaxially displaced forwardly along shaft 74 by a small amount limited byportion 198 of the clutch member 190. It will therefore be apparent,that power transmitted through the pulley 152 to the drive member 164will be transmitted directly to the power shaft 74 through the slipclutch unit 173 when engaged while the brake device 204 applies acertain amount of drag to retard rotation when engaged. It will also beapparent, that slippage of the clutch member occasioned by slightrearward axial movement relative to the conical member 194, and slippageof the drag member 213 occasioned by slight forward axial movementthereof relative to its conical member 202 will cause axial displacementof the respective members in opposite axial directions into engagementwith each other. In this fashion, the assembly 172 will automaticallyvary the amount of power transmitted to the power shaft 74 from thedrive member 164 and the amount of power absorbed in order to maintain asubstantially constant torque on the driven spindle 30 to which thepower shaft 74 is drivingly connected. The slip clutch and brakeassembly 172 is particularly designed thereby, to accommodate thevarying load applied to the spindle 30 in order to maintain a constanttension on the wire being wound. The magnetic force for alternativelyholding the clutch unit 173 engaged and the brake unit 204 engaged maybe produced by any suitable means the details of which form no part ofthe present invention, such as electromagnetic coil devices energizedthrough suitable controls manufactured for example by EatonManufacturing Co. as Control Model B2C1190 shown in its bulletin datedFebruary 15, 1959 for the Dyna-Torq clutch and brake units. It should beappreciated therefore that the axial bias exerted by springs 192 and 220on the clutch member 190 and drag member 2.18 respectively, is removedwhen the magnetic force is removed to disengage the clutch unit or thebrake unit. The foregoing identified controls involve for example a twoposition switch which may be manually or auto matically moved to a brakeposition to disengage the clutch unit and at the same time engage thebrake unit in order to reduce torque transmitted to the power outputspindle should there be an increase in tension and then moved to aclutch position for reengagement of the clutch unit and disengagement ofthe brake unit when wire tension decreases below some predeterminedvalue. In view of the slippage involved, the slip clutch and brakeassembly may be provided with facilities for removal of heat as forexample the provision of cooling fins 222 on the slip clutch member 190.

The foregoing is considered as illustrative only of the principles ofthe invention. Further, since numerous modifications and changes willreadily occur to those skilled in the art, it is not desired to limitthe invention to the exact construction and operation shown anddescribed, and accordingly all suitable modifications and equivalentsmay be resorted to falling within the scope of the invention as claimed.

What is claimed as new is as follows:

1. In a machine for respooling wire or the like on a spool, a drivemechanism for continuously rotating and cyclically reciprocating saidspool to wind the wire thereon With substantially no variations in thetension of the wire comprising, a frame, an output spindle, meansreciprocably mounting said spindle in said frame, a driven power shaftrotatably mounted by said frame, variable speed ratio drive meansdrivingly connecting said power shaft to the spindle for continuousrotation thereof, reciprocating drive means drivingly connected to saidpower shaft, means operatively connecting said reciprocating drive meansto the spindle for reciprocation thereof, a constant source of motivepower, and power controlling means operatively connecting said constantsource of motive power to the driven power shaft and responsive tovariations in loading imposed thereon to correspondingly vary powercontinuously power transmitted to the power shaft from the constantsource of motive power, said power controlling means including a slipclutch through which power is transmitted and a drag brake through whichpower as absorbed.

2. In a machine for re-spooling wire or the like on a spool, a drivemechanism for continuously rotating and cyclically reciprocating saidspool to wind the wire thereon with substantially no variations in thetension of the wire comprising, a frame, an output spindle, meansreciprocably mounting said spindle in said frame, a driven power shaftrotatably mounted by said frame, means drivingly connecting said powershaft to the spindle for continuous rotation thereof, reciprocatingdrive means drivingly connected to said power shaft, means operativelyconnecting said reciprocating drive means to the spindle forreciprocation thereof, a constant source of motive power, and powercontrolling means operatively connecting said constant source of motivepower to the driven power shaft and responsive to variations in loadingimposed thereon to correspondingly vary the power transmitted to thepower shaft from the constant source of motive power, said powercontrolling means comprising, a drive member rotatably mounted on saidpower shaft, thrust means for holding said drive member axially fixed onsaid power shaft, a slip clutch member rotatably mounted on the powershaft, a stationary brake member, a driven member frictionally engagedwith said slip clutch member, means slidably mounting said driven memberon the power shaft for rotation therewith, coupling means rotatable withthe drive member and engageable with the slip clutch member fortransmitting torque thereto, means axially biasing the slip clutchmember in one direction into engagement with the driven member whenengaged with the coupling means to increase the torque transmitted tothe power shaft, a drag member rotatable with the power shaft andaxially engageable by the slip clutch member, brake engaging meansmounted on the drag member and engageable with said stationary brakemember, and second axial biasing means for axially biasing the dragmember in said other direction to regulate absorption of torque when thebrake engaging means is engaged with the stationary brake member, saidaxial biasing means comprise, magnetic means axially holding saidcoupling means and drag engaging means in engagement with the slipclutch and brake members, respectively, and spring means axiallyopposing the bias of the magnetic means to yieldably urge the slipclutch member and the drag member in opposite axial directions.

3. The combination of claim 2 wherein said reciprocating drive meanscomprises, a spirally grooved cam shaft rotatably mounted by the frame,a high reduction drive mechanism drivingly connecting the power shaft tothe cam shaft, follower means engageable with said cam shaft for axialreciprocation therealong, a sleeve member mounted on the spindle in anaxially fixed position, and lever means interconnecting said followermeans with the sleeve member for imparting reciprocation thereto at anadjustable ratio to said reciprocation of the follower means.

4. The combination of claim 3 wherein said follower means comprises, aslide block having a bore through which said cam shaft extends, and agroove engaging element pivotally mounted within said block about apivotal axis intersecting the cam shaft, said element hav- 8 ing anarcuate tooth projecting into the bore for engagement with the camshaft, said tooth having a maximum thickness at the pivotal axis.

5. In combination with a driven power shaft, power controlling meanscomprising, a drive member rotatably mounted on said power shaft, thrustmeans for holding said drive member axially fixed on said power shaft, aslip clutch member rotatably mounted on the power shaft, a stationarybrake member, a driven member frictionally engaged with said slip clutchmember, means slidably mounting said driven member on the power shaftfor rotation therewith, coupling means rotatable with the drive memberand engageable with the slip clutch member for transmitting torquethereto, means axially biasing the slip clutch member in one directioninto engagement with the driven member when the coupling means isengaged with the slip clutch member to increase the torque transmittedto the power shaft, drag brake means rotatable with the power shaft andaxially engageable by the slip clutch member to absorb torquetransmitted to the power shaft and means on the drag brake meansengageable with said stationary brake member for axially biasing thedrag brake means in ssaid other direction to regulate absorption oftorque.

6. A slip torque transmitting device comprising, a driven power shaft, adrive member rotatably mounted on said power shaft, thrust means forholding said drive member axially fixed on said power shaft, a slipclutch member rotatably mounted on the power shaft, a driven memberfrictionally engaged with said slip clutch member, means slidablymounting said driven member on the power shaft for rotation therewith,coupling means rotatable with the drive member and engageable with theslip clutch member for transmitting torque thereto, means axiallybiasing the slip clutch member in one direction into engagement with thedriven member to increase the torque transmitted to the power shaft,said coupling means comprising a disk splined to the drive member,magnetic means axially holding said disk in engagement with the slipclutch member, and spring means axially opposing the bias of themagnetic means to yieldably urge the slip clutch member in said onedirection when transmitting torque to the slip clutch member.

7. The combination of claim 1 wherein said reciprocating drive meanscomprises, a spirally grooved cam shaft rotatably mounted by the frame,a high reduction drive mechanism drivingly connecting the power shaft tothe cam shaft, follower means engageable with said cam shaft for axialreciprocation therealong, a sleeve member mounted on the spindle in anaxially fixed position, and lever means interconnecting said followermeans with the sleeve member for imparting reciprocation thereto at anadjustable ratio to said reciprocation of the follower means.

8. The combination of claim 7 wherein said follower means comprises, aslide block having a bore through which said cam shaft extends, and agroove engaging element pivotally mounted within said block about apivotal axis intersecting the cam shaft, said element having an arcuatetooth projecting into the bore for engagement with the cam shaft, saidtooth having a maximum thickness at the pivotal axis.

9. In combination with a source of constant power and a driven memberconnected to a varying load, means for transmitting power to the drivenmember at a speed varied to maintain a constant torque comprising, apower transmitting shaft drivingly connected to the driven member, slipcoupling means mounted on said shaft and drivingly connected to thesource of constant power for transmitting power to the shaft, meansbiasing the slip coupling means in one direction when transmitting powerfor increasing the power transmitted therethrough, drag brake meansmounted on said shaft for reducing the power transmitted to the drivenmember by the shaft, means biasing said drag brake means in the otherdirection when absorbing power for regulating the power absorbed, andmeans connected to the slip coupling means for axial engagement with thedrag brake means.

10. A machine for re-spooling Wire comprising a frame, an elongatedspindle extending through said frame having a spool mounted on one endthereof, means mounting said spindle on the frame for rotation and axialreciprocation together with the spool, a power shaft rotatably mountedby the frame below the spindle, a drive mot-or drivingly connected tothe power shaft, a slip clutch mounted on said power shaft including adrive member rotatably journaled on the power shaft in an axially fixedposition, a conical driven member slidably splined to the power shaft, atorque transmitting member in frictional engagement with said drivenmember and coupling means splined to the drive member for yieldablyholding the torque transmitting member in frictional engagement with thedriven member while transmitting torque thereto, a camshaft rotatablymounted by the frame above the power shaft in parallel spaced relationto the spindle, means drivingly connecting the power shaft to thespindle at an end opposite said one end, means drivingly connecting thepower shaft to the camshaft at a selectively varied drive ratio, axialcam means mounted by the camshaft including spiral grooves formedtherein and a reversing follower assembly slidably mounted thereon forreciprocating movement, a lever member pivotally connected to thefollower assembly and the spindle, and stroke adjusting means pivotallymounting the lever member on the frame between said spindle and thecamshaft.

References Cited UNITED STATES PATENTS 1,5 45,45 1 7/ 1925 Pierson242-43 1,956,632 5/1934 Snyder 242- X 2,008,873 7/1935 Nydegger.2,147,776 2/ 1939 Mitchell. 2,271,049 l/ 1942 Treckmann et al 242452,317,290 4/ 1943 McIlvried 24245 2,401,982 6/ 1946 Springhorn 24245FOREIGN PATENTS 959,534 3/ 1957 Germany.

STANLEY N. GILREATH, Primary Examiner.

1. IN A MACHINE FOR RESPOOLING WIRE OR THE LIKE ON A SPOOL, A DRIVEMECHANISM FOR CONTINUOUSLY ROTATING AND CYCLICALLY RECIPROCATING SAIDSPOOL TO WIND THE WIRE THEREON WITH SUBSTANTIALLY NO VARIATIONS IN THETENSION OF THE WIRE COMPRISING, A FRAME, AN OUTPUT SPINDLE, MEANSRECIPROCABLY MOUNTING SAID SPINDLE IN SAID FRAME, A DRIVEN POWER SHAFTROTATABLY MOUNTED BY SAID FRAME, VARIABLE SPEED RATIO DRIVE MEANSDRIVINGLY CONNECTING SAID POWER SHAFT TO THE SPINDLE FOR CONTINUOUSROTATION THEREOF, RECIPROCATING DRIVE MEANS DRIVINGLY CONNECTED TO SAIDPOWER SHAFT, MEANS OPERATIVELY CONNECTING SAID RECIPROCATING DRIVE MEANSTO THE SPINDLE FOR RECIPROCATION THEREOF, A CONSTANT SOURCE OF MOTIVEPOWER, AND POWER CONTROLLING MEANS OPERATIVELY CONNECTING SAID CONSTANTSOURCE OF MOTIVE POWER TO THE DRIVEN POWER SHAFT AND RESPONSIVE TOVARIATIONS IN LOADING IMPOSED THEREON TO CORRESPONDINGLY VARY POWERCONTINUOUSLY POWER TRANSMITTED TO THE POWER SHAFT FROM THE CONSTANTSOURCE OF MOTIVE POWER, SAID POWER CONTROLLING MEANS INCLUDING A SLIPCLUTCH THROUGH WHICH POWER IS TRANSMITTED AND A DRAG BRAKE THROUGH WHICHPOWER AS ABSORBED.